Control system



H. DEGLON CONTROL SYSTEM May 16, 1939.

5 Sheets-Sheetl Filed May 21, l937 INVENTOR HENRY DEGLON W5 ATTORNEY H4 DEGLON CONTROL SYSTEM May 16, 1939;

Filed May 21,. 1957 5 Sheets-Sheet 2 INVENTOR HENRY DEG-LON ATTORNEY H. DEGLON CONTROL SYSTEM May 16, 1939.

Filed May 21, 1.957 5 Sheets-Sheet 3 QwM Q MM 1 I INVENTOR HEEI RY DEGLON ATTORNEY Hv DEGLON CONTROL SYSTEM May 16, 1939.

Filed May 21, 1957 5 Sheets-Sheet 4 ISI INVENTOR HENRY DEGLO-N BY ATTORNEY I I! Ill/fill! 1 1111111111,. IIIIIIIIIIIIIIIIIlI/IIII/ a l yllllllllllll/l r H. DEGLON 2,158,108 CONTROL SYSTEM Filed May 21, 1957 5 Sheets-Sheet 5 m6- 8MB IOI more IPQVE HENRY umpou ATTORNEY Patented May 16, 1939 PATENT orrlca" CONTROL SYSTEM Henry Dglon, York, Pa., assignor to S. Morgan Smith Company, York, Pa., a corporation of 7 Pennsylvania Application May 21, 1937, Serial No. 148,885

5 Claims. (01. 137144) This invention relates to prime mover control systems. It is particularly applicable to the control of impulse water wheels.

An object of the invention is to provide an improved control system inwhich the speed of the prime mover and the supply of operating fluid thereto will be properly controlled.

Anothenobject of the invention is to provide an improved control system adapted to be initiated by the operation of a control mechanism, so

that all functions necessary for the operation of the control system will be automatically performed.

Another object of the invention is to provide an improved control system for impulse water wheels having two nozzles for supplying operating fluid to the /impulse wheels'in accordance with the load, in which one of the nozzles constitutes the main nozzle and the other nozzle functions as an auxiliary nozzle which is adapted to operate in conjunction with the main nozzle only when the load is above a predetermined amount.

With the foregoing and other objects and advantages in view, the invention consists in the construction and arrangement of the several parts which will be hereinafter more fully described and claimed.

' In the accompanying drawings:

Figure 1 is a diagrammatic perspective view partly in section of a control system for impulse water wheels constructed according to the present invention, both nozzles oiv the mechanism being shown in their operative position;

Fig. 2 is a diagrammatic view partly in section of the auxiliary nozzle shown at the left in Fig; 1 and the control mechanism associated therewith; I

Fig. 3 is an enlarged elevation partly in section of the portion the control mechanism of the auxiliary nozzle shownat theextreme right in Fig. 2;

Fig. 4 is a rear elevationof the structure shown in Fig. 3;

Fig. 5 is an enlarged diagrammatic view partly in section of the operating mechanism for the main nozzle shown at the right'in Fig. 1.

Fig. 61s a similar view of the operating mechanism for the deflecting hood of the main nozzle; and

Fig. 7 is an enlarged diagrammatic perspective partly in section of the mechanismfor controlling the auxiliary nozzle shown at the left, Fig. 1.

Referring to the drawings, the apparatus may comprise an impulse wheel runner ll, mounted" of the shaft bearings being indicated at l3, Fig. 1.

The runner H is provided with the usual buckets l4 and a casing (not shown), and opposed nozzles l5, l6 controlled respectively by needle valves I1, l8 are arranged to discharge jets of 5 water against the buckets M in the manner clearly illustrated in Fig. 1.

The nozzles l5, l6 are, respectively, secured to nozzle bodies I9, 20, which may be connected with suitable supply conduits by means of flanges H, 10 22, respectively, (Figs. 1 and 2).

The needle valves l1 and I8 are, respectively, provided with stems. 23, 24 which extend, respectively, through suitable stufiing boxes 25, 26, carried by the nozzle bodies I9, 20, respectively.

In the arrangement of the parts as illustrated in the drawings, nozzle l5 constitutes the main nozzle of the turbine, while the nozzle l6 functions as an auxiliary nozzle which is adapted to operate in conjunction with the main nozzle I5 only when the load on the turbine is above a predetermined amount.

When the turbine, is in operation and the load is below a predetermined amount, nozzle l5 alone functions to supply a single jet of water for op- 25 crating the runner ll. When the load increases to a. point above that at which the maximum jet produced by the nozzle i5 is lnsuficient to take care of the load, mechanism isoperated by which the needle valve I 8 is opened so that the nozzle I6 will supply an additional jet of water to augment the supply of operating fluid as supplied by the a nozzle l5.

As long as the load remains up, both the nozf zles l5 and IE will supply two opposed .jets of water as shown in Fig. 1.

When the load decreases to a point below that at which a singlejet is sufi'icient to operate the runner, the mechanism is operated so as to close the nozzle It, sothat the nozzle l5 will function 40 alone. V The single or joint operation of the nozzles II and I5 is controlled in such a manner that there is an overlap in the stages during the operation or the turbine when, due to variations in the load,

one or two jets of the driving fluid will be supplied to the runner. 8

Associated with the nozzles l5 and I6 are suitable control mechanisms 21, 28 which are adapted to control. the operation of the respective noz- 5 zles, andthese two control mechanisms are in turn under the control of a control mechanism 29.

The three control mechanisms 21, 28 and 29 are so arranged as to automatically control the operation of the turbine, whereby the turbine will,

' operate in'the most emcient manner with one or two jets, irrespective oi. variations in the load.

As shown in Figs. 1 and 5, the control mechanism 21 may comprise a servo motor 3i including a piston 32 operating in a cylinder 33 and con-- nected to the valve stem 23.

Fluid under pressure may be admitted so as to act on either side of piston 32 and the admission of this fluid may be controlled by means of a distributing valve 34 shown as provided with a pair of piston valves 35, 33 operating in a cylinder 31. The. valves 35 and 33 may be operated bymeans of a stem 38. I

The valves 35, 33 divide the cylinder 31 into chambers 33, 43 and 4 I. Chamber 43 is connected to a source of fluid under pressure, such for instance as pressure tank 42 by a pipe 43, and chambers 33 and 4| are connected by drain pipe 44 to a sump tank 45. a

' The cylinder 31 is formed with ports 48 and 31. Port 46 is connected to chamber 48 on one side of piston 32 by a pipe 43, and port 41 is connected to chamber 53 on the other side of piston 32 by a pipe 5I.

The valves 35 and 36 are shown in their neutral position in which they lap the ports and 41 and thereby cut oil communication between the distributing valve 34 and the servo motor 3I, through the pipes 43 and 5|.

The stem 33 is connected to a floating lever 54 intermediate the ends of said lever. I

As shown in Fig. 1, one end of the lever 54 is connected to the portion of the valve stem 23 which extends beyond the cylinder 33, by means of link 55, bell crank lever 53, and link 51.

Connected to the other end of the lever 54 is a I rod 53 which, is guided in a bearing 53. The free end of the rod 58 is provided with a roller 33 which engages the face of a cam H, the roller 63 being maintained in engagement with the cam by an expansible coil spring 32, as shown in Fig. 1.

Associated with the nozzle I5 is a deflecting hood 65 which is carried by a shaft 56 journalled .in bearings 31. The shaft 33 is rotated or osclllated by mechanism to be hereinafter described so as to cause the hood to swing into or out of the path of the jet produced by the nozzle I5.

Cam 3I heretofore referred to is operated by a rod 33 slidably mounted in bearings .63. One end of the rod 33 is connected to the shaft 33 by link, 13 and lever II, so that when the deflecting hood 35 is-oscillated, cam 3i will also be moved.

As shown in Figs. 1, 2 and 7, the control mech-f l anism 28 may comprise a servo motor 3| including a piston 32 operating in a cylinder 33 and.

' connected to the valve stem 24.

means of a stem 38.

The valves as and as divide the cylinder 51 into chambers 83, 93 and ,3I. Chamber 33 is connected to the pressure tank 42 heretofore 're-' ferred to by a pipe '33, andchambersfland 3| are connected by drain pipe 34 to tank 45 heretoforereferred to.

The cylinder 81 .is provided with ports '36 and the sump 31. Port 38 is connected to chamber 33 on one side of piston 32 by a pipe 33, and port 31 is con nected to chamber I33 on the other side of piston 32 by a pipe I3i.

The valve 35 and 83 are shown in their neutral position in which they lapthe ports 33 and 3'! to thereby cut of! communication between valve 34 and servo motor 8|, through the pipes 33 and MI.

The stem 38is connected to a floating lever I34 intermediate the ends of said lever.

One end of the lever I34 is connected to the portion of the valve stem 24 which extends beyond the cylinder 33,'by means of link I35, bell "crank lever I 33, and link I31.

. The other end of the lever I34 is connected to a rod I33 which is guided in bearings Hi9.

One end of the rod. I38 is provided with a roller H3 which engages the face of a cam III, the roller being urged toward the cam face by an expansible .coil spring i I2.

Associated with the nozzle I3 is a deflecting hood H3 which is carried bya shaft H3 journalled in bearings H5. The shaft H3 is rotated or oscillated by mechanism to be hereinafter described so as to cause the hood to swing into or out 01' the path of the let produced by the nozzle I6.

Cam III heretofore referred to is operated by v a rod IIG slidably mounted in bearings II'I. One end of the rod H3 is connected to the shaft II4 by link H3 and lever II3, so that when the defleeting hood II3 isosclllated, cam Iii will also nected by a lever. I 23, a rod I2l and a lever I22,

and this leverage system is so designed that actuation of one'deflecting hood causes a corresponding operation of the other deflecting hood.

The operation'oi' the valve 34 is controlled either by cam III or by an electrically operated mechanism generally meral 33.. I

The electrically operated mechanism 33 may comprise a solenoid I24, the core I25 of which is carried by the rod I33 heretofore referred to. The energization and deenergization oi the solenoid I24 is controlled by a switch device 023, comprlsing a drum I21 loosely mounted on a shaft I23 journalled in bearings I23,'(see Fig. 7).

Mounted on the exterior oi the drum I21 is a contact plate I33 which is insulated from said drum, as indicatedat I38, Fig. 3; The contact plate I33 is adapted to receive a pair of contact lingers I3I and I32 when-the drum is in one -pOSiti0n. 7

One terminal 0! the coil of the solenoid I24'is connected to the contact finger I by a conductor I33, and theother terminal of the solenoid coil is connected to a source of current, such as a main line-conductor 4, by a conductor I33. The other contact finger I32 is connected to another main line conductor I33 by a conductor I31;

The drum-I21 is. adapted to be rotatedjthrouah' a limitedarc; or toflba-moved tosuch an extent that the fingers I3' l,fI.32 will engage the contact plate I 33 or be disengaged therefrom.

I When the lingers I3I and I32 contact with the plate I33 thefcircuit will be closed through which the solenoid I24 is energized, and when the-fingers aredlsengaged from the plate i3. the circuit through which, electric current is supplied to the solenoid I24-will be open, and, therefore,- said solenoid will be deenergized.

During the operationot the turbine, when'both of the nozzles I3, I3 are open, the solenoid I24 is deenergized and-therefore the drum I21 isso positioned thatv the fingers I3I,' I32 are disengaged from the contact plate I33, as shown in designated by the nu- Figs. 1, 2 and 3. When only the noszle I5 is u the exterior of the drum I21, as shown in Figs.

3 and 7. The locking mechanism is so construct ed as to permit rotation of the drum I21 from one position to the other by the drum operating mechanism, but prevents movement of said drum when its operating mechanism is inactive.

Any suitable mechanism may be provided for operating the drum I21. As shown in Figs. 1,

2, 3, 4 and 7, the drum operating mechanism may comprise a cam I45 fixed to the shaft I28 and 'a clutch device I46 (Fig. 4) also mounted on the shaft I28 and adapted to actuate the drum I21.

The cam I45 is formed with a notch I41 having end walls I48, I49- spaced a suitable distance apart. Disposed within the notch I41 is the extremityof an arm I50 carried rigidly by the 2 rod I2I heretofore referred to, the end of said arm being provided with a roller I5I for engag ing the walls of the notch.

Also formed in the cam I45, is a pair of notches I52, I53, which are separated by a tooth I54. A spring pressed detent I55 is adapted to engage in either ofthe notches I52, I53 and retain the cam I45 in position.

The clutch device I46 may comprise a collar having a finger I 51 projecting therefrom and disposed within an arcuate slot I58 formed in the drum I21 (see Figs. 4 and 7). I

The clutch device I46 is so constructed that rotary movement of the cam I45 is transmitted to cause a corresponding rotary movement of the drum I21.

As shown in Figs. 1 and 6, the control mechanism 29 may comprise a servo motor 12 including a piston 13 operating in a cylinder 14 and having a stem 15 extending in both directions therefrom. 1

Fluid under pressure may be admitted so as to act on either side of piston 13 and the admission of this fluid may be controlled by means of a distributing valve 16 shown as provided with a pair of piston valves 11 and 18 operating in a cylinder 19.- The valves 11 and 18 may be operated by means of a stem 80.

The valves 11 and 18 divide the cylinder 19 into chambers 92, 95 and I02. Chamber 95 is connected by a pipe I03 to the pressure tank 42 heretofore referred to, and chambers 92 and I02 are connected by pipes I23 and 44 to the sump tank 45.'

The cylinder 18 is provided with, ports I43 and I44. Port I44 is connected to chamber I85 on one side of piston 13 by a pipe I56, and port I43 is connected to chamber I59 on the other side of piston.13 by a pipe I60.

The valves 11 and 18 are shown in their neutral position in which they lap the ports I43 and I44'respectively, and thereby cut off p "3 through any suitable connection, indicatedin Fig. 1 as belted. I

The pivot I62 of the lever I6I is connected to the piston stem 15, by means of a compensating,

mechanism comprising a link I64, bell crank lever I66, and link I61, as shown in Fig. 1. In this way the distributing valve 16 is governed by the fly ball mechanism I63 and compensating mechanism. I

Piston stem 15 is also connected to the shaft 66 by a lever I65, so that when the servo mo tor 12 operates, movement of the piston 13 in either direction will cause a corresponding rotation of shaft 66. Since the two deflecting hoods 65 and 3am operatively connected to the shaft 66 the operation of said deflecting hoods will be governed by the servo motor 12.

.The sump tank 45 serves as a reservoir for containing aquantity of oil. Oil is pumped from the sump tank 45 by pump 52 (Fig. 1) and delivered to pressure tank 42. From the pressure tank 42 the oil under pressure is carried through the pipes 43, 93 and I03 to the chambers 40, 90 and 95 of the distributing valves 34, 84 and 16, respectively, so that said chambers are normally charged with oil under'pressure.

In operation, under load conditions of a predetermined amount only the main nozzle I5 will supply operating fluid to the runner II. However, when the load is above a predetermined amount, two jets, one from nozzle I5 and the other from nozzle I6 will supply operating fluid to the runner II, as shown in Fig. 1.

In this position of the device, piston valves 11v and I8, 35 and 36, 85.and 86, of the distributing valves 29, 21 and 28, respectively, are at neutral position, andneedles I1 and I8, and the deflector hoods 65and 3 are at a stand still and out of the path of the jets from the two nozzles I 5 and I6 amount, the speed of the runner I I will increase,

, thereby increasing the speed of rotation of the downwardly, ports I43 and I44 will be uncovered,

and oil under pressure from the pressure tank 42 is supplied to piston chamber I85 in operating cylinder 14, through pipe I03, chamber 95, port I 44 and pipe I56. The oil in chamber I59 is discharged through pipe I60, port I43, chamber 92, and pipes I23 and 44 into sump tank 45. Piston 13 then moves towards the left (Fig. 6) thereby turning shaft 66 and simultaneously turning the deflectors'65 and H3 and moving the cams H and III through, their' operating mechanisms which are connected to the deflector operating mechanism as has heretofore been described. The operation of cam III effects an upward movement of piston valves 85 and 86 of the control mechanism 28, and the operation of cam 6| effects a corresponding upward movement of piston valves 35 and 36 of the control mechanism 21.

Oil under pressure is then admitted into chamber 83 from the pressure tank 42, through pipe 93, chamber 90, and pipe 99.

Oil from chamber I00 is discharged through pipe IOI, chamber 9|, and pipe 94 to the'sump tank 45.

Piston'82 then moves stem 24 towards the right (Fig. 1) towards the closing position of needle I8. a

When the load decreases a predetermined 4 Oil under pressure from pressure tank 42, is admitted to chamber 48, through pipe '48, chamber 40 and pipe 49.

Oil from chamber 50 is discharged to the sump tank 45, through pipe 5|, chamber 4| and pipe 44, and piston 32 moves the stem 23 and needle I1 to the left toward the closing position of the needle I1.

Meanwhile the rod I2I moves the follower I50 towards the edge I48 of cam I45 (Fig. '1). The spring pressed detent I55 climbs tooth I54. Shaft I28 turns finger I51 of clutch I46 and face I14 of finger I51 comes in contact with face I15 of-slot I58 of the drum I21.

After the detent I55 has passed the extreme tip of the tooth I54, the spring I 16 (Figs. 3 and 7) forces the detent I55 into the notch I52.

Face I14 of finger I51 which is in contact with face I15 of the slot I58 then snaps the drum I21 and the roller of detent I40 climbs on to the tooth I11.

' After the detent I40 has moved across the tooth I11, spring I18 forces the detent I40 into the notch I42, thereby imparting a snap movement to the drum I21 and causing the contact I30 to move into engagement with the fingers I8I and- I32 so that the electric circuit is closed through which the solenoid I24 is energized.

When the solenoid is thus energized, its core I25 is pulled upwardly and the roller I I is lifted from the face of cam III. The control valve 28 is now governed or controlled by the solenoid I24 and the compensating mechanism comprising the link I05, lever I06 and link I01 connected to the rod 24 of piston 82 and nozzle I8.

Piston valves 85 and 86 in the distributing valve 84 (Figs. 1 and '7) are lifted up and remain in the up position.

Chamber 98 of the servo motor 8I (Fig. 2) remains under pressure, through pipe 89, chamber 90 of distributing valve 84 and pipe 93.

Chamber I00 remains under discharge, through pipe I04, chamber SI and pipe 94.

Piston 82, by means of the stem 24, moves needle I8 towards the-closing position and closes the nozzle I6. The time of this closing is regulated byneedle valves 63 and 64 (Fig. 2).

The position of the different parts of the regulating mechanism of the auxiliary nozzle I6 are thus shifted from the showing in Fig. 1 to the showing in Fig. 1 and the turbine operates with only the nozzle I open, and will continue to operate thusly until the load increases above'a predetermined amount.

When the load is increased above a predetermined amount the speed of the runner II will be decreased and the fly ball mechanism I63 will lift up piston valves 11 and 18 of the distributing valve 16 (see Fig. 5). v

Chamber I59 of the servo motor 12 is under pressure, being connected through pipe I60, chamber 95, and pipe I08 with the pressure supply tank 42.

Chamber I85 of the servo, motor 12 is under discharge, being connected through pipe I56,

chamber I02, and pipes I28 and 44 withthe sump Piston chamber 50 is now supplied with fluid under pressure from the pressure tank 42, through pipe 48, chamber 40and pipe 5|, and fluid in chamber 48 is discharged to the sump tank 45, through pipe 49, chamber 89, and pipe 44.

The piston 32 moves stem 28 and needle I1 toward the full open position. I

The arm I50 and its roller I5I which are attached to the rod I2I, push the end wall I49 of the notch I41 in cam I45.

The roller of the spring pressed detent I55 climbs the tooth I54 (Fig. 7) of cam I45, and after the detent I55 has passed slightly by the tip of the tooth I54, spring I16, acting on the arm of the detent I55, pulls the detent into the notch I53, thereby imparting a snap movement to the cam I45.

Shaft I28 transmits this snap movement to the clutch device I46. The spring pressed detent I40 (Fig; 3) climbs tooth I11 and spring'I18 forces the detent I40 towards notch I42, thereby imparting a snap movement to the drum I21. The contact plate I80 is thus disengaged from the contact fingers I8I and I82, thereby deenerglzing the solenoid I24. When the solenoid I24 is thus-deenergize roller IIO of the rod I08 is forced byspring II2 into contact with-the surface of the cam II I.

The downward movement of the rod I08 imparts a swinging movement to the lever I04.

The piston valves 85 and 85 of the distributing valve 84 which are operatively connected to the lever I04 by stem 88, are moved to the position in which chamber I00 of the servo motor 8| (Fig. 2) is supplied with fluid under pressure from the tank 42 and the fluid in chamber 98 is discharged to the sump tank 45.

Needle valve I8 is then moved by piston 82 towards the left (Fig. 2) to full open position so that additional'power is supplied to thedrunner II.

- The opening time of needle I8 is regulated by I needle valves 68 and 64. The piston valves of the distributing valves 34, 16 and 84 keep moving .until the needles I1 and I8 are exactly in the a proper manner as provided by the invention, the

part load efliciency of the turbine is higher than if the jets'are working simultaneously.

From the foregoing, itwill be'noted that by my invention the envelope efllciency curve has a higher eiiiciency when the load is below a prede- I termined amount and the number of jets in operation is smaller than the total number of jets. This is due to the fact that the jets in operation are working at higher load and better efllciency. 0n the other hand, when all jets are in operation for a given load,.the load per jet is smaller and consequently the efficiency lower. Having thus described my invention, what I claim is: a

1. In a controllingmechanism, the combination of a controlling element, meansfor actuating said element, speed responsive means, a valve device, power means controlled by said valve device, and means actuated by said power means for controllingthe operation of the, actuatingv means of said controlling element and comprising a cam operatively connected with said speed responsive means and normally disconnected from said actuating means and electrically actuated mechanism having a camoperated switch deviceoperatlvely-connected with said speed responsive means and having means for engaging said cam for operatively connecting the cam with said actuating means.

2- In a controlling mechanism, the combination of two controlling elements, separatemeans for individually actuating said elements, a single speed responsive means, a valve device actuated by said speed responsive means, powermeans same with said actuating means,

In a controlling mechanism, the combination of a controlling element, means for actuating said element, a device for controlling the operation of said actuating means, speed responsive means, mechanism for controlling the operation oi said control device and comprising a cam operatively connected with said speed responsive means and normally disconnected from said controlling mechanism and electrically actuated mechanism having a switch device operatively connected with said speed responsive means and having means for engaging said cam for operatively connecting the cam with said control device mechanism.

4-. In .a controlling mechanism, the combina tion of a controlling element, "fluid pressure operated means for actuating said element, a valve device for controlling the operation of said fluid pressure operated means, speed responsive means, mechanism for controlling the operation of said control valve device and comprising an electrically actuated mechanism having a switch device operatively connected with said speed responsive means and operable thereby, a cam operatively connected with said speed responsive means, and means for connecting and disconnecting said cam with said controlling mechanism 5. a control system for a plurality of sources or fluid, a main control means for controlling one source of fluid, an auxiliary control means for the other source of fluid, a governor mechanism, means for selectively controlling the operation of said. control means and comprising a cam operatively connected with. said governor mechanism and normally disconnected from said auxiliary control means, and electrically, actuated mechanism having a cam Operated switch device ,bperatively connected with said governor for connecting and disconnecting said cam with said auxiliary control means.

\ my minnow. 

